CN209944788U - Multi-temperature-section main control type liquid cooling machine - Google Patents
Multi-temperature-section main control type liquid cooling machine Download PDFInfo
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- CN209944788U CN209944788U CN201920089951.9U CN201920089951U CN209944788U CN 209944788 U CN209944788 U CN 209944788U CN 201920089951 U CN201920089951 U CN 201920089951U CN 209944788 U CN209944788 U CN 209944788U
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- 239000007788 liquid Substances 0.000 title claims abstract description 53
- 238000001816 cooling Methods 0.000 title claims description 16
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 95
- 239000000110 cooling liquid Substances 0.000 claims abstract description 58
- 238000005057 refrigeration Methods 0.000 claims abstract description 37
- 238000002156 mixing Methods 0.000 claims abstract description 23
- 239000002826 coolant Substances 0.000 claims abstract description 19
- 230000004087 circulation Effects 0.000 claims abstract description 14
- 230000006835 compression Effects 0.000 claims abstract description 12
- 238000007906 compression Methods 0.000 claims abstract description 12
- 230000001105 regulatory effect Effects 0.000 claims abstract description 12
- 239000003507 refrigerant Substances 0.000 claims description 6
- 238000004891 communication Methods 0.000 claims description 3
- 238000009825 accumulation Methods 0.000 description 17
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 4
- 238000011217 control strategy Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000002360 preparation method Methods 0.000 description 4
- 238000001514 detection method Methods 0.000 description 3
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 2
- 239000007864 aqueous solution Substances 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 239000008367 deionised water Substances 0.000 description 1
- 229910021641 deionized water Inorganic materials 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 238000000960 laser cooling Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 238000005482 strain hardening Methods 0.000 description 1
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Abstract
The utility model discloses a cold liquid machine of multi-temperature section master control formula, including making up water tank, tee bend proportional control valve, main circulating pump, heat load, auxiliary circulating pump, bypass relief valve, electric control valve, hybrid tube, refrigeration circulating pump, heat exchanger, compression refrigeration unit, coolant liquid and a plurality of temperature sensor etc. and form coolant liquid main loop, coolant liquid auxiliary loop, coolant liquid refrigeration cycle and compressor refrigeration cycle respectively. The high-temperature cooling liquid passing through the heat load is combined and controlled through four circulations to realize three-temperature-section control, namely, the high-temperature cooling liquid and the low-temperature cooling liquid from the combined water tank A are mixed and controlled at the first section in a mixing pipe through an electric regulating valve at the front section; the middle section is buffered and regulated by a combined water tank area A, an area B, an area C and a bypass pressure relief valve; and the cooling liquid in the A area and the C area of the combined water tank is proportionally mixed and output again at the tail section, so that accurate temperature control and quick response are finally realized.
Description
Technical Field
The utility model relates to a cold liquid machine field specifically is a cold liquid machine of many temperature sections master control formula with cold-storage function.
Background
In recent years, liquid cooling machines with cold accumulation function are receiving more and more attention, and particularly in heat management systems such as high-energy laser, electromagnetic pulse and high-precision electronic equipment, intermittent operation or heat load fluctuation is usually encountered, and high-precision temperature control and liquid supply are still needed. Such a liquid cooling machine has been conventionally realized by using a large-capacity cold storage water tank or a large-capacity variable load compressor unit, and has been forced to be miniaturized and energy-saving due to limitations of space, energy consumption and the like.
At present, a high-precision liquid cooling machine with a cold accumulation function usually adopts glycol aqueous solutions with different concentrations as cooling liquid according to use conditions, and the specific heat capacity of the high-precision liquid cooling machine is smaller than that of deionized water, so that the cold accumulation capacity is further deteriorated. Under the condition that the cold accumulation water tank is reduced and the cold accumulation capacity of the cooling liquid is reduced, the fluctuation of the liquid supply temperature is increased, and the requirement of temperature control precision cannot be met, for example, the temperature control precision of certain laser cooling equipment needs to meet +/-1.5 ℃, and sometimes even reaches +/-0.1 ℃ to +/-0.2 ℃. At present, a common method is realized by adopting a cold water tank, a hot water tank and a three-way proportional adjustment mode, but for high-precision equipment, due to sudden loading or unloading of a thermal load, the proportional adjustment by a group of three-way proportional adjustment is often influenced by self sensitivity and cannot be realized. For example, a heat load of 100kW, an additional heat generation of 10kW by a pump or the like, a liquid supply temperature of 25 ℃ and a liquid supply flow rate of 22m36.11L/s, the cooling liquid is 66% glycol water solution, the cold water tank has a capacity of 800kg at (-5 ℃) (cold accumulation is about 71304kJ), the hot water tank has a capacity of 200 kg. at (25 ℃) and has a temperature rise of △ t (100+ 10). times.3600/(3.3038. times.1088. times.22) of 5.0 ℃ after heat load, if the temperature of the hot water tank rises to 30 ℃, the cold energy needs to be obtained from the cold water tank at 110kJ/s, the cooling liquid is equivalent to 1.12L/s at-5 ℃ and accounts for about 18.3% of the total liquid supply flow, and the three-way proportional control valve (linear) needs to be completed within 1s at this timeThe existing quick-opening three-way proportional control valve also needs about 12s generally, and the response is almost slower by more than 2 times. The temperature of the liquid supply can easily exceed +/-2.0 ℃. Therefore, a multi-temperature-section, gradual buffering and progressive mode is needed to achieve the requirements of quick response of the liquid supply temperature and temperature control precision.
SUMMERY OF THE UTILITY MODEL
The utility model aims at solving the problem that prior art exists, provide a compact structure, have high-efficient, controllable, quick response's cold liquid machine of the main control formula of the section of temperature more, utilize anterior segment, middle section and end section control strategy and design capacity comprehensively, can realize high accuracy accuse temperature demand.
In order to achieve the above purpose, the utility model discloses the technical scheme who adopts is:
the utility model provides a cold liquid machine of multiple temperature section master control formula which characterized in that: the combined water tank is internally divided into A, B, C three areas, the A, B, C three areas are sequentially communicated, a cooling liquid outlet end of the heat load is communicated with a C area in the combined water tank through a pipeline, the A area and the C area in the combined water tank are respectively communicated with two valve ports of the three-way proportional regulating valve in a one-to-one correspondence mode through pipelines, a third valve port of the three-way proportional regulating valve is communicated with an inlet end of the main circulating pump through a pipeline, and an outlet end of the main circulating pump is communicated with a cooling liquid inlet end of the heat load through a pipeline, so that a cooling liquid main circulation is formed;
the area A of the combined water tank is also communicated with the inlet end of an auxiliary circulating pump through a pipeline, and the outlet end of the auxiliary circulating pump is respectively communicated with the area B and the area C of the combined water tank through pipelines, so that the communication of the inside of the combined water tank forms auxiliary circulation of cooling liquid;
the inlet end of the refrigeration circulating pump is communicated with the area A of the combined water tank through a pipeline, the outlet end of the refrigeration circulating pump is communicated with the cooling liquid inlet end of the heat exchanger through a pipeline, and the cooling liquid outlet end of the heat exchanger is communicated with the area A of the combined water tank through a pipeline, so that cooling liquid refrigeration circulation is formed;
the inlet end of the compression refrigeration unit is communicated with the refrigerant outlet end of the heat exchanger through a pipeline, and the outlet end of the compression refrigeration unit is communicated with the refrigerant inlet end of the heat exchanger through a pipeline, so that the refrigeration cycle of the compressor is formed.
The multi-temperature-section master control type liquid cooling machine is characterized in that: the auxiliary circulating pump in the heat load in the coolant liquid main loop, the coolant liquid auxiliary loop shares the C district of a three-way mixing tube intercommunication combination water tank, namely the coolant liquid outlet end of heat load passes through a mouth of pipe intercommunication of pipeline and mixing tube, and the outlet end of auxiliary circulating pump passes through another mouth of pipe intercommunication of pipeline and mixing tube, and the third mouth of pipe of mixing tube communicates to the C district of combination water tank.
The multi-temperature-section master control type liquid cooling machine is characterized in that: an electric regulating valve is arranged on a pipeline communicated with the C area of the combined water tank by the auxiliary circulating pump.
The multi-temperature-section master control type liquid cooling machine is characterized in that: and a bypass pressure relief valve is arranged on a pipeline communicated with the B area of the combined water tank by the auxiliary circulating pump.
The multi-temperature-section master control type liquid cooling machine is characterized in that: the initial state of the three-way proportional control valve is a C area which is communicated with the main circulating pump and the combined water tank.
The cold accumulation preparation stage of the utility model further explains as follows:
the temperature of each area of the water tank is detected firstly, and if the temperature of each area of the water tank is higher, the cooling liquid refrigeration cycle and the compressor refrigeration cycle are started, so that the cooling liquid in the area A of the combined water tank gradually reaches the set lowest cold storage temperature. When the temperature of the combined water tank A area is lower, the auxiliary circulating pump is started, and the temperature T of the cooling liquid in the area C is measured by opening the electric regulating valveCMinimum liquid supply temperature T1Cooling liquid temperature T of the B area through a bypass pressure relief valveBMinimum adjusted to low temperature coolant TAAnd then the auxiliary circulating pump stops working to finish the work of the cold accumulation stage. At the moment, the combined water tank A area and the combined water tank B area participate in cold accumulation together, and the maximum cold accumulation under the limited space is realized.
The utility model discloses a put cold working phase, further explain as follows:
the initial position of the three-way proportional control valve is firstly confirmed, namely, all cooling liquid channels are switched to a combined water tank C area. Then starting the main circulating pump to stand for T1Temperature, T2And after the temperature, the liquid supply flow and the pressure are stable and meet the requirements, the thermal load is formally started. In the adjusting process, the electric adjusting valve is adjusted at the front section, the first section mixing is realized in the mixing pipe, the cooling liquid passes through the C area → the B area → the A area at the middle section, and the three-way proportional adjusting valve is adjusted at the tail section, so that the fluctuation of the liquid supply temperature is controlled within the design range. In a specific control strategy, millisecond-level (such as 10 ms-100 ms) temperature or rate detection can be adopted, and PID, fuzzy control theory, specific algorithm and the like are applied, so that the temperature control precision is further improved.
The utility model has the advantages that:
1. the utility model discloses the cushioning effect of make full use of multi-temperature section control technique and water tank realizes high accuracy accuse temperature demand.
2. The utility model discloses make full use of current governing valve combines the detection and the control strategy of millisecond level, realizes quick response.
3. The utility model discloses a structure can be miniaturized, the modularization, can effectively satisfy high energy, heat density, intermittent type nature's heat dissipation demand.
4. The utility model discloses under the condition is not opened in the coolant liquid main loop, realize the biggest cold-storage.
5. The utility model discloses the input cost is lower relatively, easily realizes.
Drawings
Fig. 1 is a schematic view of the structure principle of the present invention.
Detailed Description
The present invention will be further explained with reference to the drawings and examples.
As shown in fig. 1, a multi-temperature-section main control type liquid cooling machine comprises a combined water tank 1, a heat load 4, a three-way proportional control valve 2, a main circulating pump 3, a heat exchanger 21, a refrigerating circulating pump 20 and a compression refrigerating unit 22, wherein the combined water tank 1 is divided into A, B, C three areas 1.1, 1.2 and 1.3, a, B, C, three areas 1.1, 1.2 and 1.3 are sequentially communicated, a cooling liquid outlet end of the heat load 4 is communicated with an area C1.3 in the combined water tank 1 through a pipeline, the area A1.1 and the area C1.3 in the combined water tank are also correspondingly communicated with two valve ports of the three-way proportional control valve 2 one by one through pipelines respectively, a third valve port of the three-way proportional control valve 2 is communicated with an inlet end of the main circulating pump 3 through a pipeline, and an outlet end of the main circulating pump 3 is communicated with a cooling liquid inlet end of the heat load 4 through a pipeline, so that a main cooling liquid circulation is formed, as shown in fig. 1;
the area A1.1 of the combined water tank 1 is also communicated with the inlet end of an auxiliary circulating pump 10 through a pipeline, the outlet end of the auxiliary circulating pump 10 is respectively communicated with the area B1.2 and the area C1.3 of the combined water tank 1 through pipelines, and therefore the communication inside the combined water tank 1 forms auxiliary cooling liquid circulation, as shown in figure 1;
an inlet end of the refrigeration circulating pump 20 is communicated with the area A1.1 of the combined water tank 1 through a pipeline, an outlet end of the refrigeration circulating pump 20 is communicated with a cooling liquid inlet end of the heat exchanger 21 through a pipeline, and a cooling liquid outlet end of the heat exchanger 21 is communicated with the area A1.1 of the combined water tank 1 through a pipeline, so that a cooling liquid refrigeration cycle is formed, as shown in FIG. 1;
the inlet end of the compression refrigeration unit 22 communicates with the refrigerant outlet end of the heat exchanger 21 through a pipeline, and the outlet end of the compression refrigeration unit 22 communicates with the refrigerant inlet end of the heat exchanger 21 through a pipeline, thereby constituting a compressor refrigeration cycle, as shown in fig. 1.
The auxiliary circulating pump 10 in the heat load 4 and the auxiliary circulating pump 10 in the auxiliary circulating of the cooling liquid in the main circulating of the cooling liquid share a three-way mixing pipe 13 to be communicated with the C area 1.3 of the combined water tank 1, namely, the cooling liquid outlet end of the heat load 4 is communicated with one pipe orifice of the mixing pipe 13 through a pipeline, the outlet end of the auxiliary circulating pump 10 is communicated with the other pipe orifice of the mixing pipe 13 through a pipeline, and the third pipe orifice of the mixing pipe 13 is communicated to the C area 1.3 of the combined water tank 1.
An electric control valve 12 is arranged on a pipeline of the auxiliary circulating pump 10 communicated with the C area 1.3 of the combined water tank 1.
A bypass pressure relief valve 11 is arranged on a pipeline of the auxiliary circulating pump 10 communicated with the B area 1.2 of the combined water tank 1.
The initial state of the three-way proportional control valve 2 is a C area 1.3 which is communicated with the main circulating pump and the combined water tank.
The utility model discloses a make up water tank 1, tee bend proportional control valve 2, main circulating pump 3, heat load 4, auxiliary circulating pump 10, bypass pressure relief valve 11, electrical control valve 12, hybrid tube 13, refrigeration circulating pump 20, heat exchanger 21, compression refrigeration unit 22, coolant liquid and a plurality of temperature sensor etc. constitute, form coolant liquid main loop, coolant liquid auxiliary loop, coolant liquid refrigeration cycle and compressor refrigeration cycle respectively, through high temperature coolant liquid T of heat load 42And low-temperature cooling liquid T from a combined water tank A area 1.1AThe first mixing is realized in the mixing pipe 13 and enters the C area 1.3 of the combined water tank for further mixing to form TCThe cooling liquid enters the combined water tank B area 1.2 through a through hole at the lower part of the combined water tank C area 1.3 and is mixed with the low-temperature cooling liquid T from the bypass pressure relief valve 11AIs remixed to form TBThe cooling liquid enters the combined water tank A area 1.1 through the through hole at the upper part of the combined water tank B area 1.2, and the cooling liquid T at the combined water tank A area 1.1 is cooledAAnd zone C1.3 Coolant TCThe liquid is mixed again by the three-way proportional control valve 2 to form the required liquid supply temperature T1And cooling the liquid to finish the main circulation control of the cooling liquid. The core of the front section of the multi-temperature section is controlled by an electric regulating valve 12, the middle section of the multi-temperature section is buffered and regulated by the capacity of each area of the combined water tank and a bypass pressure relief valve 11, and the tail section of the multi-temperature section is controlled by a tee joint proportional regulating valve 2.
The auxiliary circulation of the cooling liquid is to utilize an auxiliary circulating pump 10 to suck low-temperature cooling liquid T from a region 1.1 of the combined water tank AAThen, the outlet is divided into 2 paths, the 1 st path is connected with the inlet end of an electric control valve 12, the outlet end of the electric control valve 12 is connected with the inlet end of a mixing pipe 13, and the outlet end of the mixing pipe 13 is connected with a combined water tank C area; the 2 nd path is connected with the inlet end of a bypass pressure relief valve 11, and the outlet end of the bypass pressure relief valve 11 is connected with a combined water tank B area 1.2. In the cold storage preparation phase, the temperature T of the cooling liquid in the C area 1.3 is adjusted by the electric adjusting valve 12CLowest adjustment to T1The temperature T of the cooling liquid in the B area 1.2 is adjusted by a bypass pressure relief valve 11BLowest adjustment to TAAnd the cold accumulation work is finished.
The combined water tank 1 consists of an A area 1.1, a B area 1.2 and a C area 1.3 which respectively form a TA、TB、TCThree temperatures, wherein the temperature of the A area 1.1 is the lowest, are realized by the cooling liquid refrigeration cycle and the compressor refrigeration cycle together; the temperature of the C area 1.3 is highest, and the heat load 4 is operated by high-temperature cooling liquid T2And a low-temperature cooling liquid TAMixing the first section; the combined water tank A area 1.1 and the combined water tank B area 1.2 are communicated at the upper part, the combined water tank B area 1.2 and the combined water tank C area 1.3 are communicated at the lower part, the combined water tank A and the combined water tank C area are connected at the lower part outside by a three-way proportional control valve 2, and the initial position of the valve is only communicated with the combined water tank C area and a main circulating pump 3.
The outlet of the compression refrigeration unit 22 is connected with 1 inlet of the heat exchanger 21, and 1 outlet of the heat exchanger 21 is connected with the inlet of the compression refrigeration unit 22 to form a compression refrigeration cycle; the outlet of the refrigeration circulating pump 20 is connected with the other 1 inlet of the heat exchanger 21, and the other 1 outlet of the heat exchanger 21 is connected with the inlet of the combined water tank A area 1.1 to form the refrigeration circulation of the cooling liquid.
The initial position of the three-way proportional control valve 2 is communicated with a main circulating pump 3 and a combined water tank C area 1.3.
The specific work generally comprises a cold accumulation preparation phase and a cold release working phase:
in the cold accumulation preparation stage, the temperature of each area of the water tank is detected by a temperature sensor, if the temperature of each area of the water tank is higher, the cooling liquid refrigeration cycle and the compressor refrigeration cycle are started, so that the cooling liquid in the area A1.1 of the combined water tank gradually reaches the set lowest cold accumulation temperature TA. When the temperature of the combined water tank A area 1.1 is lower, the auxiliary circulating pump 10 is started, and the temperature T of the cooling liquid in the area C1.3 is adjusted by opening the electric adjusting valve 12CMinimum liquid supply temperature T1The temperature T of the cooling liquid in the B area 1.2 is adjusted by a bypass pressure relief valve 11BMinimum adjusted to low temperature coolant TAAnd then the auxiliary circulating pump stops working to finish the work of the cold accumulation stage. At the moment, the combined water tank A area 1.1 and the combined water tank B area 1.2 participate in cold accumulation together, and the maximum cold accumulation under the limited space is realized.
In the cold-discharging working stage, the initial position of the three-way proportional control valve 2 is firstly confirmed, namely, all cooling liquid channels are switched to a combined water tank C area 1.3. Then the main circulation pump 3 is started to wait for T1Temperature, T2The temperature, the liquid supply flow and the pressure are stable and meet the requirementsThen, the thermal load 4 is formally turned on. In the adjusting process, the electric adjusting valve 12 is adjusted at the front section, the first section mixing is realized in the mixing pipe 13, the cooling liquid passes through the C area 1.3 → the B area 1.2 → the A area 1.1 at the middle section, the three-way proportional adjusting valve 3 is adjusted at the tail section, and finally the fluctuation of the liquid supply temperature is controlled within the design range. In a specific control strategy, millisecond-level (such as 10 ms-100 ms) temperature or rate detection can be adopted, and PID, fuzzy control theory, specific algorithm and the like are applied, so that the temperature control precision is further improved.
The combined water tank A area 1.1, the combined water tank B area 1.2 and the combined water tank C area 1.3 can be completed by adopting an integral structure with a partition plate in the middle or can be completed by adopting 3 relatively independent water tanks which are connected through an intermediate pipeline.
If the auxiliary circulation pump 10 is implemented by an inverter pump, the electric control valve 12 can be omitted for adjustment.
The above embodiments are only preferred embodiments of the present invention, but the present invention is not limited to the above embodiments, and any obvious modifications to the above embodiments without departing from the principle of the present invention will fall within the protection scope of the present invention and the appended claims.
Claims (5)
1. The utility model provides a cold liquid machine of multiple temperature section master control formula which characterized in that: the combined water tank is internally divided into A, B, C three areas, the A, B, C three areas are sequentially communicated, a cooling liquid outlet end of the heat load is communicated with a C area in the combined water tank through a pipeline, the A area and the C area in the combined water tank are respectively communicated with two valve ports of the three-way proportional regulating valve in a one-to-one correspondence mode through pipelines, a third valve port of the three-way proportional regulating valve is communicated with an inlet end of the main circulating pump through a pipeline, and an outlet end of the main circulating pump is communicated with a cooling liquid inlet end of the heat load through a pipeline, so that a cooling liquid main circulation is formed;
the area A of the combined water tank is also communicated with the inlet end of an auxiliary circulating pump through a pipeline, and the outlet end of the auxiliary circulating pump is respectively communicated with the area B and the area C of the combined water tank through pipelines, so that the communication of the inside of the combined water tank forms auxiliary circulation of cooling liquid;
the inlet end of the refrigeration circulating pump is communicated with the area A of the combined water tank through a pipeline, the outlet end of the refrigeration circulating pump is communicated with the cooling liquid inlet end of the heat exchanger through a pipeline, and the cooling liquid outlet end of the heat exchanger is communicated with the area A of the combined water tank through a pipeline, so that cooling liquid refrigeration circulation is formed;
the inlet end of the compression refrigeration unit is communicated with the refrigerant outlet end of the heat exchanger through a pipeline, and the outlet end of the compression refrigeration unit is communicated with the refrigerant inlet end of the heat exchanger through a pipeline, so that the refrigeration cycle of the compressor is formed.
2. The multi-temperature-section main control type liquid cooling machine according to claim 1, characterized in that: the auxiliary circulating pump in the heat load in the coolant liquid main loop, the coolant liquid auxiliary loop shares the C district of a three-way mixing tube intercommunication combination water tank, namely the coolant liquid outlet end of heat load passes through a mouth of pipe intercommunication of pipeline and mixing tube, and the outlet end of auxiliary circulating pump passes through another mouth of pipe intercommunication of pipeline and mixing tube, and the third mouth of pipe of mixing tube communicates to the C district of combination water tank.
3. The multi-temperature-section main control type liquid cooling machine according to claim 1, characterized in that: an electric regulating valve is arranged on a pipeline communicated with the C area of the combined water tank by the auxiliary circulating pump.
4. The multi-temperature-section main control type liquid cooling machine according to claim 1, characterized in that: and a bypass pressure relief valve is arranged on a pipeline communicated with the B area of the combined water tank by the auxiliary circulating pump.
5. The multi-temperature-section main control type liquid cooling machine according to claim 1, characterized in that: the initial state of the three-way proportional control valve is a C area which is communicated with the main circulating pump and the combined water tank.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920089951.9U CN209944788U (en) | 2019-01-21 | 2019-01-21 | Multi-temperature-section main control type liquid cooling machine |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201920089951.9U CN209944788U (en) | 2019-01-21 | 2019-01-21 | Multi-temperature-section main control type liquid cooling machine |
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| CN209944788U true CN209944788U (en) | 2020-01-14 |
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| CN201920089951.9U Withdrawn - After Issue CN209944788U (en) | 2019-01-21 | 2019-01-21 | Multi-temperature-section main control type liquid cooling machine |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109724280A (en) * | 2019-01-21 | 2019-05-07 | 合肥天鹅制冷科技有限公司 | A kind of cold liquid machine of multiple temperature sections main control type |
-
2019
- 2019-01-21 CN CN201920089951.9U patent/CN209944788U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109724280A (en) * | 2019-01-21 | 2019-05-07 | 合肥天鹅制冷科技有限公司 | A kind of cold liquid machine of multiple temperature sections main control type |
| CN109724280B (en) * | 2019-01-21 | 2024-02-20 | 合肥天鹅制冷科技有限公司 | Multi-temperature Duan Zhukong type liquid cooling machine |
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